US20070227677A1 - Cordless window covering - Google Patents
Cordless window covering Download PDFInfo
- Publication number
- US20070227677A1 US20070227677A1 US11/392,340 US39234006A US2007227677A1 US 20070227677 A1 US20070227677 A1 US 20070227677A1 US 39234006 A US39234006 A US 39234006A US 2007227677 A1 US2007227677 A1 US 2007227677A1
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- Prior art keywords
- spring
- rotary
- drum
- gear
- rotary drum
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
-
- E—FIXED CONSTRUCTIONS
- E06—DOORS, WINDOWS, SHUTTERS, OR ROLLER BLINDS IN GENERAL; LADDERS
- E06B—FIXED OR MOVABLE CLOSURES FOR OPENINGS IN BUILDINGS, VEHICLES, FENCES OR LIKE ENCLOSURES IN GENERAL, e.g. DOORS, WINDOWS, BLINDS, GATES
- E06B9/00—Screening or protective devices for wall or similar openings, with or without operating or securing mechanisms; Closures of similar construction
- E06B9/24—Screens or other constructions affording protection against light, especially against sunshine; Similar screens for privacy or appearance; Slat blinds
- E06B9/26—Lamellar or like blinds, e.g. venetian blinds
- E06B9/28—Lamellar or like blinds, e.g. venetian blinds with horizontal lamellae, e.g. non-liftable
- E06B9/30—Lamellar or like blinds, e.g. venetian blinds with horizontal lamellae, e.g. non-liftable liftable
- E06B9/32—Operating, guiding, or securing devices therefor
- E06B9/322—Details of operating devices, e.g. pulleys, brakes, spring drums, drives
-
- E—FIXED CONSTRUCTIONS
- E06—DOORS, WINDOWS, SHUTTERS, OR ROLLER BLINDS IN GENERAL; LADDERS
- E06B—FIXED OR MOVABLE CLOSURES FOR OPENINGS IN BUILDINGS, VEHICLES, FENCES OR LIKE ENCLOSURES IN GENERAL, e.g. DOORS, WINDOWS, BLINDS, GATES
- E06B9/00—Screening or protective devices for wall or similar openings, with or without operating or securing mechanisms; Closures of similar construction
- E06B9/24—Screens or other constructions affording protection against light, especially against sunshine; Similar screens for privacy or appearance; Slat blinds
- E06B9/26—Lamellar or like blinds, e.g. venetian blinds
- E06B9/28—Lamellar or like blinds, e.g. venetian blinds with horizontal lamellae, e.g. non-liftable
- E06B9/30—Lamellar or like blinds, e.g. venetian blinds with horizontal lamellae, e.g. non-liftable liftable
- E06B9/32—Operating, guiding, or securing devices therefor
- E06B9/322—Details of operating devices, e.g. pulleys, brakes, spring drums, drives
- E06B2009/3222—Cordless, i.e. user interface without cords
Definitions
- This invention relates to window coverings.
- this invention relates to cordless window coverings where a user does not need to manipulate a control cord to raise or lower the window covering.
- a window covering typically contains a number of light blocking sections that extend horizontally across the width of a window space or other architectural opening. These light blocking sections can take a myriad of forms such as that of cellular shades, slats in a Venetian blind, and the flat sheet of a Roman shade.
- at least one suspension cord hangs down through the light blocking sections from the head rail to a ballast portion, such as a bottom rail.
- the window covering is raised and lowered by a user manually raising or lowering the suspension cord. After the covering is drawn to the desired height, a brake mechanism or cord lock engages the suspension cord to hold the suspension cord and correspondingly the window covering in place at the desired height.
- cordless window coverings As an alternative to conventional control cords, cordless window coverings have been developed.
- a cordless window covering operates differently than a conventional window covering in that the window covering is raised and lowered by direct manipulation of the window covering itself rather than through manipulation of a suspension cord by the user.
- the cordless window covering employs suspension cords extending from the head rail through the light blocking elements and connected to the ballast portion or bottom rail.
- a constant force is applied to bias the suspension cord towards the head rail. This force counters the downward gravitational force caused by the weight of the ballast portion and light blocking elements, which is constant, such that the portion of the window covering is maintained at equilibrium.
- the constant upward force biasing the suspension cord toward the head rail is typically maintained by use of a coiled spring such as a spiral spring or a constant force spring.
- the smooth raising and lowering function of a cordless window covering relies heavily on continually balancing the weight of the window covering with an upwards force exerted by the spring on the suspension cords.
- the upward force exerted by the spring does not balance the downward gravitational weight of the window covering, the window covering will not remain in the desired position.
- the ballast portion of the window covering is lifted upwards or pulled downwards by a user, the spring ideally exerts sufficient force to instantaneously balance the weight of the window covering in order for the window covering to remain at the adjusted position.
- a cord lock or brake that engages the suspension cord may be used to provide a frictional force to resist excessive upward or downward forces.
- One disadvantage of the conventional cordless window covering is that the length of the coiled spring limits the range of expansion of the window covering. Since the weight of the window covering is constant, maintaining a constant force requires the spring to be within its linear response range throughout the entire range of motion for the window covering. In ranges where the spring response is nonlinear, no equilibrium between the spring force and the weight of the window covering can be reached.
- the present invention is a cordless window covering with a differentially geared suspension mechanism adapted to translate a linear length of cord wound to a reduced amount of extension of a spring.
- a differentially geared suspension mechanism adapted to translate a linear length of cord wound to a reduced amount of extension of a spring.
- the entire range of motion of a window covering may be accommodated without exceeding the range of extension of the coil corresponding to its linear response range, i.e., equilibrium force.
- a larger range of window covering extension can be accommodated by a given size spring.
- a preferred embodiment of the window covering also includes a ballast element, such as a bottom rail, and at least one light blocking element. At least one suspension cord is associated with the ballast element and a suspension mechanism.
- the suspension mechanism preferably mounted in a head rail, is composed of a first rotary drum adapted to wind and unwind the suspension cord and a second rotary drum housing a spring.
- the spring is mounted at one end to an axle and is mounted at the second end to the second rotary drum.
- a transmission system operatively connects the first rotary drum and at least of the axle or the second rotary drum.
- the transmission system can be composed of a system of gears, belts, or other drive means.
- extension and contraction of the spring can occur in three ways.
- the inner end of the spring may be fixed from rotation while the outer end of the spring attached to the drum rotates.
- the end attached to the drum may be fixed from rotation while the inner end of spring is extended and contracted by rotation of the axle.
- both the axle and the drum rotate, but at different rates. This causes the inner end and the outer end of the spring rotate at different rates, causing extension and contraction of the spring by virtue of their relative movement.
- the transmission system creates a differential in the rotational displacement between the first rotary drum and the relative rotational displacement between the two ends of the spring.
- the first rotary drum rotates at a greater rotational rate than the relative rotational movement of the two ends of the spring.
- the first rotary drum rotates faster than the spring uncoils. This results in a greater length of cord that can be deployed for a given revolution of the spring.
- This reduction in the spring's necessary range of extension enables the spring to remain within its linear response range throughout the movement range of the suspension cord. Accordingly, undesired variations in the force provided by the spring to balance and resist the weight of window covering are minimized.
- FIG. 2A is a perspective view of the cordless window covering of FIG. 1 in the extended position
- FIG. 2B is a perspective view of the cordless window covering of FIG. 1 in the retracted position
- FIG. 4 is a schematic top view of the suspension mechanism of FIG. 3 ;
- FIG. 5 is an exploded view of the suspension mechanism of FIG. 3 ;
- FIG. 6 is a cutaway view of the winding gear assembly in the suspension mechanism
- FIG. 6A is an exploded view of the winding gear assembly of FIG. 6 ;
- FIG. 6B is a cutaway exploded view of the winding gear assembly of FIG. 6 ;
- FIG. 7 is an exploded view of the loading gear assembly in the suspension mechanism
- FIG. 8 is a perspective view of the suspension mechanism of FIG. 3 ;
- FIG. 9 is a perspective view of a suspension mechanism of an alternate embodiment
- FIG. 10 is an exploded view of the suspension mechanism of FIG. 9 ;
- FIG. 11 is a perspective view of a suspension mechanism of another alternate embodiment.
- FIG. 12 is an exploded view of the suspension mechanism of FIG. 11 .
- the window covering includes a head rail 12 and a ballast element 14 .
- Ballast element 14 may be a bottom rail and is preferably of sufficient weight to keep the window covering properly extended in the window space.
- the window covering 10 also has at least one light blocking element 16 . These light blocking elements 16 are shown in FIGS. 2A and 2B as cellular structures, but they may also take the form of slats, sheets, or other suitable structures.
- At least one suspension cord 18 connects the head rail 12 with the ballast element 14 .
- at least two suspension cords are used to maintain symmetrical balance across the width of the window covering 10 .
- the suspension cords 18 are associated to the light blocking elements 16 . It should be understood that the light blocking elements 16 may be directly connected to the suspension cords 18 , but suspension cords 18 may also be indirectly connected to the light blocking element 16 through intermediate structures such as cord loops or pass through light blocking element 16 . Light blocking elements 16 are also preferably connected to the ballast element 14 and the suspension mechanism 30 by direct or indirect connections via suspension cords 18 .
- the suspension cords would be associated with the light blocking element and may or may not be connected to the ballast element.
- FIGS. 3 and 4 show a preferred embodiment of suspension mechanism 30 .
- Suspension mechanism 30 can be mounted in the head rail 12 or the ballast element 14 .
- the suspension mechanism 30 is connected to the ballast element 14 by suspension cords 18 or directly by virtue of being mounted in the ballast element 14 .
- the suspension mechanism 30 is mounted inside the head rail 12 .
- the suspension mechanism 30 includes two subassemblies, a winding gear assembly 40 and a loading gear assembly 60 . These assemblies are mounted onto a bottom plate 32 and may be further secured by a top plate 34 , pins 36 , and side housings 38 .
- the winding gear assembly 40 and the loading gear assembly 60 are linked by a transmission system of gears described herein.
- a suspension cord 18 is wound and unwound by the winding gear assembly 40 .
- the winding gear assembly 40 is capable of being rotated in either direction depending on whether a suspension cord 18 is being wound or unwound, i.e. whether the window covering is being raised or lowered.
- the suspension mechanism 30 has two winding gear assemblies 40 a and 40 b and two loading gear assemblies 60 a and 60 b .
- Suspension cord 18 a cooperates with winding gear assembly 40 a and loading gear assembly 60 a
- cord 18 b cooperates with winding gear assembly 40 b and loading gear assembly 60 b .
- Winding gear assembly 40 a and 40 b are identical, as are loading gear assemblies 60 a and 60 b.
- the winding gear assembly 40 comprises a first winding gear 42 and a second winding gear 44 .
- the second winding gear 44 serves as a differential gear relative to first winding gear 42 .
- the first winding gear 42 and the second winding gear 44 are spaced by a rotary winding drum 46 .
- rotary winding drum 46 is composed of two nesting parts 43 and 45 that are joined to the first winding gear 42 and the second winding gear 44 respectively. It should be understood that the rotary winding drum 46 may also be integrally connected to only the first winding gear 42 or the second winding gear 44 .
- the rotary winding drum 46 may alternatively take the configuration of a housing integral to a winding gear and a groove for receiving the lip of the housing in the opposite winding gear.
- the rotary winding drum 46 has a surface 47 suitable for winding and unwinding a suspension cord 18 .
- first winding gear 42 , second winding gear 44 , and the rotary winding drum 46 are in coaxial alignment with each other.
- first winding gear 42 and the second winding gear 44 are in alignment with each other and are configured to rotate at different rotational displacements. Specifically, the second winding gear 44 rotates at a slower rotational displacement than the first winding gear 42 .
- Differential rotation displacement between the first winding gear 42 and the second winding gear 44 can be accomplished in a number of ways.
- a pinion gear 48 is integrally connected to the axis of the first winding gear 42 .
- Pinion gear 48 is in engagement with a set of planetary gears 50 .
- the planetary gears 50 engage with a ring gear 52 , which rotates with the second winding gear 44 .
- the ring gear 52 may also be integrally joined with the second winding gear 44 .
- Rotation of the first winding gear 42 drives the rotation of the second winding gear 44 through the pinion gear 48 and planetary gears 50 .
- Pinion gear 48 and planetary gears 50 are chosen so that the rotation of the first winding gear 42 drives the rotation of second winding gear 44 in the same direction as the first winding gear 42 but at a slower rate.
- Pinion gear 48 and planetary gears 50 thus serve to create a differential rotational displacement between first winding gear 42 and second winding gear 44 . Since the first winding gear 42 and the rotary winding drum surface 47 are integrally connected in the configuration shown in FIGS. 6A and 6B , both the first winding gear 42 and the rotary winding drum surface 47 rotate together at the same rotational displacement relative to each other and at a differential rotational displacement relative to the second winding gear 44 .
- the differential rotational displacement ratio between the first winding gear 42 a and the second winding gear 44 a can be controlled by selection of the pinion gear 48 and planetary gears 50 .
- the differential rotational displacement ratio in turns translates to a reduced movement range of the coiled spring 68 that is needed in relation to the movement of the suspension cord.
- the expansion range of the window covering is increased by a factor related to the differential gear ratio.
- This use of differential gear ratios reduces the needed extension range of the spring for a given expansion range of a window covering.
- This spring extension range reduction is preferable since it ensures that the spring remains in its linear response range during the entire range of the window covering's motion. This in turn prevents undesired variations in the resisting force to the constant downward force caused by the gravitational weight of the window covering that may otherwise be caused by excessive spring extension.
- the loading gear assembly 60 comprises a first loading gear 62 and a second loading gear 64 .
- a rotary loading drum 66 Disposed between the first loading gear 62 and the second loading gear 64 is a rotary loading drum 66 , which is rotatably mounted on an axle 76 .
- Rotary loading drum 66 is similar in size and radius as the rotary winding drum 46 .
- the rotary loading drum 66 is integrally connected to the first loading gear 62 .
- the axle 76 is rotatable relative to the rotary loading drum 66 and is connected to the second loading gear 64 .
- the first loading gear 62 , the second loading gear 64 , and the rotary loading drum 66 are coaxially assembled with one another.
- a spring or other resilient means such as coiled spring 68 or other constant force spring, is mounted inside the rotary loading drum 66 .
- spring 68 has an inner end 70 and an outer end 72 .
- the inner end 70 of the spring 68 is fixedly secured to a slot 74 on axle 76 .
- At the outer end 72 of spring 68 is a tab that is fixedly secured to a slot 78 disposed on the rotary loading drum 66 .
- the first loading gear 62 and the second loading gear 64 rotate are free to rotate at different rotational displacements relative to each other.
- FIG. 8 shows the relationship between the winding gear assembly 40 a and the loading gear assembly 60 a in the suspension mechanism 30 .
- the first winding gear 42 a is in engagement with the first loading gear 62 a .
- the second winding gear 44 a is in engagement with the second loading gear 64 a . Since the second winding gear 44 a rotates at a slower rotational displacement than first winding gear 42 a , the second loading gear 64 a also rotates at a slower rotational displacement relative to second loading gear 64 a .
- the differential rotation displacements between the first loading gear 62 and the second loading gear 64 result in a relative displacement between inner end 70 and outer end 72 of spring 68 . This results in a storing or releasing of tension on the spring through extension and contraction.
- spring 68 may be secured or connected to the first loading gear 62 and the second loading gear 64 in other ways. Spring 68 may be chosen so that the spring is in its linear response range over the entire range of movement of the window covering.
- suspension cord 18 a When the user pulls down on the bottom rail or ballast portion of the window covering, suspension cord 18 a is unwound from the rotary winding drum 46 a and away from suspension mechanism 30 .
- This force imbalance unwinds the cord 18 a from rotary winding drum 46 a , inducing a counterclockwise rotation of rotary winding drum 46 a in winding gear assembly 40 a . Since rotary winding drum 46 a is fixedly connected to first winding gear 42 a , the first winding gear 42 a also rotates in a counterclockwise direction.
- the second winding gear 44 a also rotates counterclockwise. Since the pinion gear 48 and the planetary gears 50 are selected to create a differential gear ratio between first winding gear 42 a and second winding gear 44 a , the second winding gear 44 a rotates at a lower rotational displacement than first winding gear 42 a . The counterclockwise rotation of first winding gear 42 a and second winding gear 44 a also drives the clockwise rotation of first loading gear 62 a and second loading gear 64 a respectively.
- the first loading gear 62 a and second loading gear 64 a are capable of different rotation displacements relative to each other. Since the first winding gear 42 a rotates at a higher rotational displacement than second winding gear 44 a , that movement is transferred to the loading gear assembly 60 a , resulting in the first loading gear 62 a having a higher rotational displacement than the second loading gear 64 a.
- This differential in rotational displacement causes coil spring 68 to be extended, but at a lesser rotational displacement than the rotation of the rotary winding drum 46 a and rotary loading drum 66 a .
- the rotary winding drum 46 a rotates faster than the relative rotational displacement between the inner end 70 and the outer end 72 of spring 68 .
- the coiled spring contracts at an effective rotational displacement slower than the rotational displacement of the rotary winding drum 46 a .
- the differential ratio between the rotation of the rotary winding drum 46 a and the effective rotational displacement of the spring is between about 1.5 to 1 and 5 to 1. In an exemplary embodiment, the differential ratio is 3 to 1.
- the rotary winding drum 46 a completes three revolutions. This differential permits the rotary winding drum 46 a to deploy and retract greater lengths of the suspension cord relative to the corresponding length and contraction of spring 68 .
- the second winding gear assembly 40 b and the second loading gear assembly 60 b operate in the same manner in response to movement of suspension cord 18 b , with the rotational directions reversed.
- the first loading gear assembly 60 a and the second loading gear assembly 60 b may be in engagement with each other as shown in FIG. 8 .
- By engaging the two loading gear assemblies 60 a and 60 b additional tension is brought to bear on both suspension cords 18 a and 18 b .
- the engagement of the two loading gear assemblies synchronizes their rotation, ensuring symmetrical deployment and retraction of suspension cords 18 a and 18 b.
- suspension mechanism 30 The operation of the suspension mechanism 30 is reversible.
- a user lifts the ballast portion of the window covering, some slack in suspension cord 18 a is created. Without the downward force on suspension cord 18 a resisting the contraction of spring 68 , spring 68 contracts and induces the rotation of the loading gear assembly 60 a and the winding gear assembly 40 a . This in turn causes rotation of rotary winding drum 46 a to take up the slack in suspension cord 18 a until the cord is taut.
- FIGS. 9 and 10 show an alternate preferred embodiment of the suspension mechanism of the present invention.
- the suspension mechanism 130 includes two winding gear assemblies 140 and two loading gear assemblies 160 held together between bottom plate 132 and top plate 134 by pins 136 and side housings 138 .
- winding gear assembly 140 comprises a first winding gear 142 and a second winding gear 144 spaced by a rotary winding drum 146 for winding and unwinding a suspension cord 118 .
- Rotary winding drum 146 is composed of two nesting parts 143 and 145 that are joined to the first winding gear 142 and the second winding gear 144 respectively.
- differential rotational displacements between the first winding gear 142 and the second winding gear 144 is achieved through the use of planetary gears 150 and a ring gear 152 .
- the loading gear assembly 160 comprises a first loading gear 162 and a second loading gear 164 with a rotary loading drum 166 .
- Rotary loading drum 166 is integrally connected to the first loading gear 162 and is rotatably mounted relative to axle 176 connected to the second loading gear 164 .
- a spring 168 is mounted inside the rotary loading drum 168 .
- the inner end of 170 of spring 168 is fixedly secured to the axle 176 , while the outer end 172 is fixedly secured to a slot 178 disposed on the rotary loading drum 166 .
- the operation of winding gear assembly 140 and loading gear assembly 160 is substantially similar to that previously described in relation to the embodiment of FIG. 8 .
- the differential rotational displacements between the first winding gear 142 and the second winding gear 144 translates to a relative rotational displacement between the inner end 170 and the outer end 172 of spring 168 that is less than the rotational displacement of rotary winding drum 146 .
- revolution of rotary winding drum 146 completes several revolutions, thus extending longer lengths of cord 118 per length of spring extension.
- Central gear assembly 180 disposed between the two loading gear assemblies 160 is a central gear assembly 180 .
- Central gear assembly 180 has a central gear 182 attached to a central rotary drum 186 .
- Central gear 182 engages loading gears 162 of the adjacent loading assemblies 160 .
- a central axle 196 is mounted on central base 184 , which itself is non-rotatably mounted to the bottom plate 132 .
- Disposed within the housing of the central rotary drum 186 is a central spring 188 with an inner end 190 and an outer end 192 .
- the inner end 190 of central spring 188 is fixedly secured to central axle 196 by slot 194 .
- the outer end 192 of central spring 188 is fixedly secured to the central rotary drum 186 by a slot 198 disposed on the central rotary drum 186 .
- central spring 188 Since central base 184 and central axle 196 does not rotate, the inner end of central spring 188 is rotatably fixed. Rotation of the central gear 182 tensions central spring 188 by only movement of the outer end 192 . Since the central spring 188 is extended and contracted only by movement of the outer end 192 rather than both the outer 192 and the inner end 190 as in the loading gear assemblies 160 , the central spring 188 is capable of providing tighter tension as the central gear assembly 180 rotates. This is particularly useful to strengthen the tension exerted through suspension cords 118 in larger sized window shades.
- FIGS. 11 and 12 show yet another alternate preferred embodiment of the present invention.
- suspension mechanism 230 includes winding gear assembly 240 and loading gear assembly 260 .
- Winding gear assembly 240 is composed of a winding gear 242 connected to a winding drum rotary winding drum 246 .
- the winding gear assembly 240 is mounted by axle pin 236 between bottom plate 232 and top plate 234 .
- Loading gear assembly 260 is composed of a rotary loading drum 266 integrally connected to a loading gear 262 .
- Mounted inside the rotary loading drum 266 is a constant force spring 268 with an inner end 270 and an outer end 272 .
- the inner end 270 of spring 268 is secured to a slot 274 on axle 276 disposed rotary loading drum base 264 .
- the outer end 272 of spring 268 is fixedly secured to a slot 278 disposed on the rotary loading drum 266 .
- a differential rotational displacement between the rotary winding drum 246 and the spring 268 is obtained by changing relative number of teeth between winding gear 242 and loading gear 262 .
- winding gear 242 rotates at a greater rate than loading gear 262 .
- a pinion gear 248 may be disposed in engagement between the winding gear 242 and loading gear 262 . Rotation of the winding gear 242 in one direction thus causes rotation of the loading gear in the same direction through the action of pinion gear 248 .
- the winding gear assembly 240 rotates as suspension cord 218 is pulled away from the suspension mechanism 230 .
- This causes the winding gear 242 to rotate with the rotary winding drum 246 .
- the rotation of winding gear 242 induces the rotation of pinion gear 248 and loading gear 262 .
- Rotary loading drum base 264 is stationary, fixing the inner end 270 of the spring 268 from rotation. Rotation of the loading gear 262 and rotary loading drum 266 thus tensions the spring 268 by rotating the outer end 272 of spring 268 relative to the rotatably fixed inner end 270 .
- winding gear 242 rotates for several revolutions for each revolution of the loading gear 262 .
- gear ratio between the winding gear 242 and the loading gear 262 is 3 to 1
- rotary winding drum 246 completes three revolutions for every revolution of the rotary loading drum 266 .
- a length of suspension cord 218 equal to three circumferences of rotary winding drum 246 is deployed. This permits the suspension cord to be deployed over a greater range with a smaller extension of the spring.
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- Engineering & Computer Science (AREA)
- Structural Engineering (AREA)
- Architecture (AREA)
- Civil Engineering (AREA)
- Window Of Vehicle (AREA)
- Curtains And Furnishings For Windows Or Doors (AREA)
- Storing, Repeated Paying-Out, And Re-Storing Of Elongated Articles (AREA)
Abstract
A cordless window covering having a differential suspension mechanism. The suspension mechanism is composed of a first rotary drum for winding and unwinding the suspension cord of a window covering and a second rotary drum housing a spring with one end connected to the second rotary drum and the other end of the spring connected to an axle. Rotation of the first rotary drum and at least one end of the spring are linked by a transmission system. In operation, the transmission system creates a differential rotation rate between the first rotary drum and the relative rotation rate of the two ends of the spring. In this manner, a greater length of cord can be deployed for with a shorter length of spring extension.
Description
- This invention relates to window coverings. In particular, this invention relates to cordless window coverings where a user does not need to manipulate a control cord to raise or lower the window covering.
- Window coverings are well known in the art. A window covering typically contains a number of light blocking sections that extend horizontally across the width of a window space or other architectural opening. These light blocking sections can take a myriad of forms such as that of cellular shades, slats in a Venetian blind, and the flat sheet of a Roman shade. In these conventional window coverings, at least one suspension cord hangs down through the light blocking sections from the head rail to a ballast portion, such as a bottom rail. The window covering is raised and lowered by a user manually raising or lowering the suspension cord. After the covering is drawn to the desired height, a brake mechanism or cord lock engages the suspension cord to hold the suspension cord and correspondingly the window covering in place at the desired height.
- As an alternative to conventional control cords, cordless window coverings have been developed. A cordless window covering operates differently than a conventional window covering in that the window covering is raised and lowered by direct manipulation of the window covering itself rather than through manipulation of a suspension cord by the user. Like a conventional window covering, the cordless window covering employs suspension cords extending from the head rail through the light blocking elements and connected to the ballast portion or bottom rail. A constant force is applied to bias the suspension cord towards the head rail. This force counters the downward gravitational force caused by the weight of the ballast portion and light blocking elements, which is constant, such that the portion of the window covering is maintained at equilibrium. The constant upward force biasing the suspension cord toward the head rail is typically maintained by use of a coiled spring such as a spiral spring or a constant force spring.
- The smooth raising and lowering function of a cordless window covering relies heavily on continually balancing the weight of the window covering with an upwards force exerted by the spring on the suspension cords. When the upward force exerted by the spring does not balance the downward gravitational weight of the window covering, the window covering will not remain in the desired position. When the ballast portion of the window covering is lifted upwards or pulled downwards by a user, the spring ideally exerts sufficient force to instantaneously balance the weight of the window covering in order for the window covering to remain at the adjusted position.
- When a constant force spring is used, the force exerted by the spring to resist uncoiling is constant since the change in the radius of curvature is constant. When other resilient means or non-constant force springs are used, a cord lock or brake that engages the suspension cord may be used to provide a frictional force to resist excessive upward or downward forces.
- One disadvantage of the conventional cordless window covering is that the length of the coiled spring limits the range of expansion of the window covering. Since the weight of the window covering is constant, maintaining a constant force requires the spring to be within its linear response range throughout the entire range of motion for the window covering. In ranges where the spring response is nonlinear, no equilibrium between the spring force and the weight of the window covering can be reached.
- What is needed is an improved cordless window covering and suspension mechanism that reduces the range of extension required on a coiled spring while permitting a window covering to operate in the full desired range of motion. The present invention meets these desires and overcomes the shortcomings of the prior art.
- The present invention is a cordless window covering with a differentially geared suspension mechanism adapted to translate a linear length of cord wound to a reduced amount of extension of a spring. In other words, by translating the length of the suspension cord of the window covering into a lesser linear distance of coil extension, the entire range of motion of a window covering may be accommodated without exceeding the range of extension of the coil corresponding to its linear response range, i.e., equilibrium force. Additionally, a larger range of window covering extension can be accommodated by a given size spring. A preferred embodiment of the window covering also includes a ballast element, such as a bottom rail, and at least one light blocking element. At least one suspension cord is associated with the ballast element and a suspension mechanism.
- The suspension mechanism, preferably mounted in a head rail, is composed of a first rotary drum adapted to wind and unwind the suspension cord and a second rotary drum housing a spring. The spring is mounted at one end to an axle and is mounted at the second end to the second rotary drum. A transmission system operatively connects the first rotary drum and at least of the axle or the second rotary drum. The transmission system can be composed of a system of gears, belts, or other drive means.
- With the inner end of the spring mounted to the axle and the outer end of the spring mounted to the second rotary drum, extension and contraction of the spring can occur in three ways. First, the inner end of the spring may be fixed from rotation while the outer end of the spring attached to the drum rotates. Secondly, the end attached to the drum may be fixed from rotation while the inner end of spring is extended and contracted by rotation of the axle. Finally, both the axle and the drum rotate, but at different rates. This causes the inner end and the outer end of the spring rotate at different rates, causing extension and contraction of the spring by virtue of their relative movement.
- In operation, the transmission system creates a differential in the rotational displacement between the first rotary drum and the relative rotational displacement between the two ends of the spring. With similarly sized drums, the first rotary drum rotates at a greater rotational rate than the relative rotational movement of the two ends of the spring. In other words, the first rotary drum rotates faster than the spring uncoils. This results in a greater length of cord that can be deployed for a given revolution of the spring. This reduction in the spring's necessary range of extension enables the spring to remain within its linear response range throughout the movement range of the suspension cord. Accordingly, undesired variations in the force provided by the spring to balance and resist the weight of window covering are minimized.
- In the drawings,
-
FIG. 1 is a front view of a preferred embodiment of the cordless window covering in accordance with the present invention; -
FIG. 2A is a perspective view of the cordless window covering ofFIG. 1 in the extended position; -
FIG. 2B is a perspective view of the cordless window covering ofFIG. 1 in the retracted position; -
FIG. 3 is a side view of the suspension mechanism of the cordless window ofFIG. 1 ; -
FIG. 4 is a schematic top view of the suspension mechanism ofFIG. 3 ; -
FIG. 5 is an exploded view of the suspension mechanism ofFIG. 3 ; -
FIG. 6 is a cutaway view of the winding gear assembly in the suspension mechanism; -
FIG. 6A is an exploded view of the winding gear assembly ofFIG. 6 ; -
FIG. 6B is a cutaway exploded view of the winding gear assembly ofFIG. 6 ; -
FIG. 7 is an exploded view of the loading gear assembly in the suspension mechanism; -
FIG. 8 is a perspective view of the suspension mechanism ofFIG. 3 ; -
FIG. 9 is a perspective view of a suspension mechanism of an alternate embodiment; -
FIG. 10 is an exploded view of the suspension mechanism ofFIG. 9 ; -
FIG. 11 is a perspective view of a suspension mechanism of another alternate embodiment; and -
FIG. 12 is an exploded view of the suspension mechanism ofFIG. 11 . - The invention disclosed herein is susceptible to embodiment in many different forms. The embodiments shown in the drawings and described in detail below is only for illustrative purposes. The disclosure is intended as an exemplification of the principles and features of the invention, but does not limit the invention to the illustrated embodiments.
- Referring to
FIGS. 1, 2A and 2B, a preferred embodiment of the cordless window covering 10 according to the present invention is shown. The window covering includes ahead rail 12 and aballast element 14.Ballast element 14 may be a bottom rail and is preferably of sufficient weight to keep the window covering properly extended in the window space. The window covering 10 also has at least onelight blocking element 16. Theselight blocking elements 16 are shown inFIGS. 2A and 2B as cellular structures, but they may also take the form of slats, sheets, or other suitable structures. - At least one
suspension cord 18 connects thehead rail 12 with theballast element 14. Preferably, at least two suspension cords are used to maintain symmetrical balance across the width of the window covering 10. Thesuspension cords 18 are associated to thelight blocking elements 16. It should be understood that thelight blocking elements 16 may be directly connected to thesuspension cords 18, butsuspension cords 18 may also be indirectly connected to thelight blocking element 16 through intermediate structures such as cord loops or pass through light blockingelement 16.Light blocking elements 16 are also preferably connected to theballast element 14 and thesuspension mechanism 30 by direct or indirect connections viasuspension cords 18. - While the following discussion is in terms of bottom-up style window coverings, it should also be understood that the present invention is suitable for use in top-down style window coverings. In a top-down style window covering, the suspension cords would be associated with the light blocking element and may or may not be connected to the ballast element.
-
FIGS. 3 and 4 show a preferred embodiment ofsuspension mechanism 30.Suspension mechanism 30 can be mounted in thehead rail 12 or theballast element 14. Thesuspension mechanism 30 is connected to theballast element 14 bysuspension cords 18 or directly by virtue of being mounted in theballast element 14. In the illustrated embodiment, thesuspension mechanism 30 is mounted inside thehead rail 12. Thesuspension mechanism 30 includes two subassemblies, a windinggear assembly 40 and a loading gear assembly 60. These assemblies are mounted onto abottom plate 32 and may be further secured by atop plate 34, pins 36, and side housings 38. The windinggear assembly 40 and the loading gear assembly 60 are linked by a transmission system of gears described herein. - A
suspension cord 18 is wound and unwound by the windinggear assembly 40. The windinggear assembly 40 is capable of being rotated in either direction depending on whether asuspension cord 18 is being wound or unwound, i.e. whether the window covering is being raised or lowered. In window coverings with twosuspension cords 18 a and 18 b as shown inFIG. 4 , thesuspension mechanism 30 has two windinggear assemblies 40 a and 40 b and two loading gear assemblies 60 a and 60 b.Suspension cord 18 a cooperates with windinggear assembly 40 a and loading gear assembly 60 a, while cord 18 b cooperates with winding gear assembly 40 b and loading gear assembly 60 b. Windinggear assembly 40 a and 40 b are identical, as are loading gear assemblies 60 a and 60 b. - As can be more clearly seen in
FIGS. 5 and 6 , the windinggear assembly 40 comprises a first windinggear 42 and a second windinggear 44. As will be further explained, the second windinggear 44 serves as a differential gear relative to first windinggear 42. The first windinggear 42 and the second windinggear 44 are spaced by arotary winding drum 46. As shown inFIGS. 6A and 6B ,rotary winding drum 46 is composed of twonesting parts gear 42 and the second windinggear 44 respectively. It should be understood that therotary winding drum 46 may also be integrally connected to only the first windinggear 42 or the second windinggear 44. Furthermore, therotary winding drum 46 may alternatively take the configuration of a housing integral to a winding gear and a groove for receiving the lip of the housing in the opposite winding gear. Therotary winding drum 46 has asurface 47 suitable for winding and unwinding asuspension cord 18. To minimize bulk and conserve space, first windinggear 42, second windinggear 44, and therotary winding drum 46 are in coaxial alignment with each other. - In this particular embodiment, the first winding
gear 42 and the second windinggear 44 are in alignment with each other and are configured to rotate at different rotational displacements. Specifically, the second windinggear 44 rotates at a slower rotational displacement than the first windinggear 42. Differential rotation displacement between the first windinggear 42 and the second windinggear 44 can be accomplished in a number of ways. In a preferred embodiment, apinion gear 48 is integrally connected to the axis of the first windinggear 42.Pinion gear 48 is in engagement with a set ofplanetary gears 50. Theplanetary gears 50 engage with aring gear 52, which rotates with the second windinggear 44. Thering gear 52 may also be integrally joined with the second windinggear 44. - Rotation of the first winding
gear 42 drives the rotation of the second windinggear 44 through thepinion gear 48 andplanetary gears 50.Pinion gear 48 andplanetary gears 50 are chosen so that the rotation of the first windinggear 42 drives the rotation of second windinggear 44 in the same direction as the first windinggear 42 but at a slower rate.Pinion gear 48 andplanetary gears 50 thus serve to create a differential rotational displacement between first windinggear 42 and second windinggear 44. Since the first windinggear 42 and the rotary windingdrum surface 47 are integrally connected in the configuration shown inFIGS. 6A and 6B , both the first windinggear 42 and the rotary windingdrum surface 47 rotate together at the same rotational displacement relative to each other and at a differential rotational displacement relative to the second windinggear 44. - It should be noted that the differential rotational displacement ratio between the first winding gear 42 a and the second winding gear 44 a can be controlled by selection of the
pinion gear 48 andplanetary gears 50. The differential rotational displacement ratio in turns translates to a reduced movement range of the coiledspring 68 that is needed in relation to the movement of the suspension cord. Thus for a given spring length, the expansion range of the window covering is increased by a factor related to the differential gear ratio. This use of differential gear ratios reduces the needed extension range of the spring for a given expansion range of a window covering. This spring extension range reduction is preferable since it ensures that the spring remains in its linear response range during the entire range of the window covering's motion. This in turn prevents undesired variations in the resisting force to the constant downward force caused by the gravitational weight of the window covering that may otherwise be caused by excessive spring extension. - Referring to
FIG. 7 , the loading gear assembly 60 comprises afirst loading gear 62 and asecond loading gear 64. Disposed between thefirst loading gear 62 and thesecond loading gear 64 is arotary loading drum 66, which is rotatably mounted on anaxle 76.Rotary loading drum 66 is similar in size and radius as therotary winding drum 46. As shown, therotary loading drum 66 is integrally connected to thefirst loading gear 62. Theaxle 76 is rotatable relative to therotary loading drum 66 and is connected to thesecond loading gear 64. Like the windinggear assembly 40, thefirst loading gear 62, thesecond loading gear 64, and therotary loading drum 66 are coaxially assembled with one another. - A spring or other resilient means, such as coiled
spring 68 or other constant force spring, is mounted inside therotary loading drum 66. As seen inFIG. 7 ,spring 68 has aninner end 70 and an outer end 72. Theinner end 70 of thespring 68 is fixedly secured to aslot 74 onaxle 76. At the outer end 72 ofspring 68 is a tab that is fixedly secured to aslot 78 disposed on therotary loading drum 66. Thefirst loading gear 62 and thesecond loading gear 64 rotate are free to rotate at different rotational displacements relative to each other. -
FIG. 8 shows the relationship between the windinggear assembly 40 a and the loading gear assembly 60 a in thesuspension mechanism 30. The first winding gear 42 a is in engagement with thefirst loading gear 62 a. Similarly, the second winding gear 44 a is in engagement with the second loading gear 64 a. Since the second winding gear 44 a rotates at a slower rotational displacement than first winding gear 42 a, the second loading gear 64 a also rotates at a slower rotational displacement relative to second loading gear 64 a. The differential rotation displacements between thefirst loading gear 62 and thesecond loading gear 64 result in a relative displacement betweeninner end 70 and outer end 72 ofspring 68. This results in a storing or releasing of tension on the spring through extension and contraction. Those of ordinary skill in the art will understand thatspring 68 may be secured or connected to thefirst loading gear 62 and thesecond loading gear 64 in other ways.Spring 68 may be chosen so that the spring is in its linear response range over the entire range of movement of the window covering. - The operation of the
suspension mechanism 30 will now be described. When the user pulls down on the bottom rail or ballast portion of the window covering,suspension cord 18 a is unwound from the rotary winding drum 46 a and away fromsuspension mechanism 30. The force exerted onsuspension cord 18 a in a direction away from thesuspension mechanism 30 exceeds the force exerted by thespring 68 in the loading gear assembly 60. This force imbalance unwinds thecord 18 a from rotary winding drum 46 a, inducing a counterclockwise rotation of rotary winding drum 46 a in windinggear assembly 40 a. Since rotary winding drum 46 a is fixedly connected to first winding gear 42 a, the first winding gear 42 a also rotates in a counterclockwise direction. - Owing to
pinion gear 48 and the planetary gears 50 (as previously shown inFIGS. 6 a and 6 b) within the windinggear assembly 40 a, the second winding gear 44 a also rotates counterclockwise. Since thepinion gear 48 and theplanetary gears 50 are selected to create a differential gear ratio between first winding gear 42 a and second winding gear 44 a, the second winding gear 44 a rotates at a lower rotational displacement than first winding gear 42 a. The counterclockwise rotation of first winding gear 42 a and second winding gear 44 a also drives the clockwise rotation offirst loading gear 62 a and second loading gear 64 a respectively. As explained previously, thefirst loading gear 62 a and second loading gear 64 a are capable of different rotation displacements relative to each other. Since the first winding gear 42 a rotates at a higher rotational displacement than second winding gear 44 a, that movement is transferred to the loading gear assembly 60 a, resulting in thefirst loading gear 62 a having a higher rotational displacement than the second loading gear 64 a. - It will be recalled from
FIG. 7 that theinner end 70 ofspring 78 is mounted onaxle 76, which rotates together with second loading gear 64 a. Similarly the outer end 72 ofspring 68 is mounted on the rotary loading drum 66 a, which rotates together withfirst loading gear 62 a. While both theaxle 76 and the rotary loading drum 66 a rotate in the same direction, the rotary loading drum 66 a rotates at a higher rotational displacement relative to the rotation displacement ofaxle 76. Consequently, the outer end 72 ofspring 68 thus has a higher rotational displacement than theinner end 70. Owing to the rotation of theaxle 76, rotation of thespring 68 can be defined by the relative rotational displacement between theinner end 70 and the outer end of the 72 is less than the overall rotational displacement of outer end 72. - This differential in rotational displacement causes
coil spring 68 to be extended, but at a lesser rotational displacement than the rotation of the rotary winding drum 46 a and rotary loading drum 66 a. In other words, the rotary winding drum 46 a rotates faster than the relative rotational displacement between theinner end 70 and the outer end 72 ofspring 68. As a result, the coiled spring contracts at an effective rotational displacement slower than the rotational displacement of the rotary winding drum 46 a. In a preferred embodiment, the differential ratio between the rotation of the rotary winding drum 46 a and the effective rotational displacement of the spring is between about 1.5 to 1 and 5 to 1. In an exemplary embodiment, the differential ratio is 3 to 1. Put another way, for one contracting revolution of thecoil spring 68, the rotary winding drum 46 a completes three revolutions. This differential permits the rotary winding drum 46 a to deploy and retract greater lengths of the suspension cord relative to the corresponding length and contraction ofspring 68. - The second winding gear assembly 40 b and the second loading gear assembly 60 b operate in the same manner in response to movement of suspension cord 18 b, with the rotational directions reversed. The first loading gear assembly 60 a and the second loading gear assembly 60 b may be in engagement with each other as shown in
FIG. 8 . By engaging the two loading gear assemblies 60 a and 60 b, additional tension is brought to bear on bothsuspension cords 18 a and 18 b. Furthermore, the engagement of the two loading gear assemblies synchronizes their rotation, ensuring symmetrical deployment and retraction ofsuspension cords 18 a and 18 b. - The operation of the
suspension mechanism 30 is reversible. When a user lifts the ballast portion of the window covering, some slack insuspension cord 18 a is created. Without the downward force onsuspension cord 18 a resisting the contraction ofspring 68,spring 68 contracts and induces the rotation of the loading gear assembly 60 a and the windinggear assembly 40 a. This in turn causes rotation of rotary winding drum 46 a to take up the slack insuspension cord 18 a until the cord is taut. -
FIGS. 9 and 10 show an alternate preferred embodiment of the suspension mechanism of the present invention. In this embodiment, thesuspension mechanism 130 includes two windinggear assemblies 140 and twoloading gear assemblies 160 held together betweenbottom plate 132 andtop plate 134 by pins 136 and side housings 138. Similar to the previous embodiment, windinggear assembly 140 comprises a first windinggear 142 and a second windinggear 144 spaced by arotary winding drum 146 for winding and unwinding asuspension cord 118.Rotary winding drum 146 is composed of twonesting parts 143 and 145 that are joined to the first windinggear 142 and the second windinggear 144 respectively. Similar to the embodiment ofFIG. 5 , differential rotational displacements between the first windinggear 142 and the second windinggear 144 is achieved through the use ofplanetary gears 150 and aring gear 152. - The
loading gear assembly 160 comprises afirst loading gear 162 and asecond loading gear 164 with arotary loading drum 166.Rotary loading drum 166 is integrally connected to thefirst loading gear 162 and is rotatably mounted relative to axle 176 connected to thesecond loading gear 164. Aspring 168 is mounted inside therotary loading drum 168. The inner end of 170 ofspring 168 is fixedly secured to the axle 176, while the outer end 172 is fixedly secured to aslot 178 disposed on therotary loading drum 166. The operation of windinggear assembly 140 andloading gear assembly 160 is substantially similar to that previously described in relation to the embodiment ofFIG. 8 . In other words, the differential rotational displacements between the first windinggear 142 and the second windinggear 144 translates to a relative rotational displacement between theinner end 170 and the outer end 172 ofspring 168 that is less than the rotational displacement ofrotary winding drum 146. Thus for every revolution of extension byspring 168, revolution ofrotary winding drum 146 completes several revolutions, thus extending longer lengths ofcord 118 per length of spring extension. - As shown in
FIG. 9 , disposed between the twoloading gear assemblies 160 is acentral gear assembly 180.Central gear assembly 180 has acentral gear 182 attached to acentral rotary drum 186.Central gear 182 engages loading gears 162 of theadjacent loading assemblies 160. Acentral axle 196 is mounted oncentral base 184, which itself is non-rotatably mounted to thebottom plate 132. Disposed within the housing of thecentral rotary drum 186 is acentral spring 188 with aninner end 190 and anouter end 192. Theinner end 190 ofcentral spring 188 is fixedly secured tocentral axle 196 byslot 194. Theouter end 192 ofcentral spring 188 is fixedly secured to thecentral rotary drum 186 by aslot 198 disposed on thecentral rotary drum 186. - Since
central base 184 andcentral axle 196 does not rotate, the inner end ofcentral spring 188 is rotatably fixed. Rotation of thecentral gear 182 tensionscentral spring 188 by only movement of theouter end 192. Since thecentral spring 188 is extended and contracted only by movement of theouter end 192 rather than both the outer 192 and theinner end 190 as in theloading gear assemblies 160, thecentral spring 188 is capable of providing tighter tension as thecentral gear assembly 180 rotates. This is particularly useful to strengthen the tension exerted throughsuspension cords 118 in larger sized window shades. -
FIGS. 11 and 12 show yet another alternate preferred embodiment of the present invention. In this embodiment,suspension mechanism 230 includes windinggear assembly 240 andloading gear assembly 260. Windinggear assembly 240 is composed of a windinggear 242 connected to a winding drumrotary winding drum 246. The windinggear assembly 240 is mounted byaxle pin 236 betweenbottom plate 232 andtop plate 234.Loading gear assembly 260 is composed of arotary loading drum 266 integrally connected to aloading gear 262. Mounted inside therotary loading drum 266 is aconstant force spring 268 with aninner end 270 and anouter end 272. Theinner end 270 ofspring 268 is secured to aslot 274 onaxle 276 disposed rotaryloading drum base 264. Theouter end 272 ofspring 268 is fixedly secured to aslot 278 disposed on therotary loading drum 266. - A differential rotational displacement between the
rotary winding drum 246 and thespring 268 is obtained by changing relative number of teeth between windinggear 242 andloading gear 262. Thus in rotation, windinggear 242 rotates at a greater rate thanloading gear 262. Apinion gear 248 may be disposed in engagement between the windinggear 242 andloading gear 262. Rotation of the windinggear 242 in one direction thus causes rotation of the loading gear in the same direction through the action ofpinion gear 248. - In the operation of this embodiment, the winding
gear assembly 240 rotates assuspension cord 218 is pulled away from thesuspension mechanism 230. This causes the windinggear 242 to rotate with therotary winding drum 246. The rotation of windinggear 242 induces the rotation ofpinion gear 248 andloading gear 262. Rotaryloading drum base 264 is stationary, fixing theinner end 270 of thespring 268 from rotation. Rotation of theloading gear 262 androtary loading drum 266 thus tensions thespring 268 by rotating theouter end 272 ofspring 268 relative to the rotatably fixedinner end 270. - Owing to the difference in radii between winding
gear 242 andloading gear 262, windinggear 242 rotates for several revolutions for each revolution of theloading gear 262. For example, where the gear ratio between the windinggear 242 and theloading gear 262 is 3 to 1,rotary winding drum 246 completes three revolutions for every revolution of therotary loading drum 266. In other words, for every revolution of thespring 268 in therotary loading drum 266, a length ofsuspension cord 218 equal to three circumferences ofrotary winding drum 246 is deployed. This permits the suspension cord to be deployed over a greater range with a smaller extension of the spring. - The foregoing description and the drawings are illustrative of the present invention and are not to be taken as limiting. Still other variants and rearrangements of parts within the spirit and scope of the present invention are possible and will be readily apparent to those skilled in the art.
Claims (30)
1. A window covering comprising:
a ballast element;
an adjustable light blocking element connected to the ballast element;
at least one suspension cord associated with the light blocking element; and
a suspension mechanism connected to the suspension cord to adjust the light blocking element, the suspension mechanism having:
a first rotary drum adapted to wind and unwind the suspension cord;
a spring having a first end, and a second end mounted on an axle, the first end being rotatable with respect to the second end; and
a transmission system operatively connecting the first rotary drum and at least one end of the spring to transmit a rotating movement at a differential rotation rate between the first rotary drum and the one end of the spring such that the first rotary drum rotates at a faster rate than an effective rotational displacement of the spring.
2. The window covering of claim 1 , wherein the spring is a constant-force spring.
3. The window covering of claim 1 , wherein the window covering further comprises a second rotary drum with the one end being the first end of the spring connected to the second rotary drum.
4. The window covering of claim 3 , wherein the transmission system links at least the first rotary drum and the first end of the spring.
5. The window covering of claim 4 , wherein the transmission system also links the first rotary drum and the axle.
6. The window covering of claim 5 , wherein the rotation of the first rotary drum drives the rotation of the second rotary drum and the rotation of the axle such that rotational displacement of the first end of the spring connected to the second rotary drum is greater than the rotational displacement of the second end of the spring mounted on the axle.
7. The window covering of claim 1 , wherein the ratio between the rotational displacement of the first rotary drum and the effective rotational displacement of the spring ranges from about 1.5 to 1 to about 5 to 1.
8. The window covering of claim 4 , wherein the axle is fixed from rotation.
9. The window covering of claim 8 , wherein the transmission system comprises a winding gear connected to the first rotary drum and a loading gear connected to the second rotary drum, the winding gear and the loading gear configured to rotate at different rotational displacements to set a differential rotation rate between the first and second rotary drums.
10. The window covering of claim 9 , wherein the winding gear is connected to the loading gear by a pinion gear.
11. The window covering of claim 8 , wherein the ratio in the differential rotation rate between the first rotary drum and the second rotary drum is greater than about 1.5 to 1 and less than about 5 to 1.
12. A window covering comprising:
a ballast element;
at least one light blocking element connected to the ballast element;
a suspension cord associated with the light blocking element;
a suspension mechanism engagingly connected to the suspension cord, the suspension mechanism comprising:
a spring having a first end and a second end;
a rotary winding drum for winding and unwinding the suspension cord;
a rotary loading drum connected to the first end of the spring and driven in rotation by a rotation of the rotary winding drum; and
a rotary axle connected to the second end of the spring and rotating at a different rate relative to the rotary loading drum such that the rotary winding drum has a rotation rate greater than an effective rotational displacement of the spring.
13. The window covering of claim 12 , wherein the spring is a constant-force spring.
14. The window covering of claim 12 , wherein the suspension mechanism mounted in a head rail of the window covering.
15. The window covering of claim 12 , wherein the ratio between the rotational displacement of the rotary winding drum and the effective rotational displacement of the spring ranges from about 1.5 to 1 to about 5 to 1.
16. The window covering of claim 12 , wherein the rotary winding drum is further connected to a second winding gear and the axle is further connected to a second loading gear;
the first winding gear and the second winding gear are operatively connected by a planetary gear in differential gearing engagement.
the first winding gear being operatively connected with the first loading gear; and
the second winding gear being operatively connected with the second loading gear.
17. A window covering comprising:
a ballast element;
an adjustable light blocking element connected to the ballast element;
at least two suspension cords associated with the light blocking element; and
a suspension mechanism connected to the suspension cords to adjust the light blocking element, the suspension mechanism having:
two rotary winding drums each respectively adapted to wind and unwind a respective suspension cord;
two rotary loading drums adapted for each respective suspension cord, each rotary loading drum further having an axle and a constant force spring having a first end and a second end, the first end of the spring being connected to the rotary loading drum and the second end of the spring being mounted on the axle;
a transmission system operatively connecting the rotary winding drum and at least one end of the spring to transmit a rotating movement at a differential rate between the rotary winding drum and the one end of the spring; and
each rotary loading drum is in operative engagement with each other and rotates at about the same rotational displacement rate.
18. The window covering of claim 17 , wherein each rotary loading drum is connected by operative engagement to a central rotary drum disposed therebetween in operative engagement with each rotary loading drum, the central rotary drum further having a central axle and a central spring having a first end connected to the central rotary drum and a second end mounted on the central axle.
19. The window covering of claim 17 , wherein the central axle is fixed from rotation.
20. A suspension mechanism for use in a window covering with a suspension cord, the suspension mechanism comprising:
a first rotary drum adapted to wind and unwind the suspension cord;
a spring having a first end, and a second end mounted on an axle, the first end being rotatable with respect to the second end; and
a transmission system operatively connecting the first rotary drum and at least one end of the spring to transmit a rotating movement at a differential rate between the first rotary drum and the one end of the spring such that the first rotary drum rotates at a faster rate than an effective rotational displacement of the spring.
21. The suspension mechanism of claim 20 , wherein the spring is a constant-force spring.
22. The suspension mechanism of claim 20 , wherein the suspension mechanism further comprises a second rotary drum with the one end being the first end of the spring connected to the second rotary drum.
23. The suspension mechanism of claim 22 , wherein the transmission system links at least the first rotary drum and the first end of the spring.
24. The suspension mechanism of claim 23 , wherein the transmission system also links the first rotary drum and the axle.
25. The suspension mechanism of claim 24 , wherein the rotation of the first rotary drum drives the rotation of the second rotary drum and the rotation of the axle such that rotational displacement of the first end of the spring connected to the second rotary drum is greater than the rotational displacement of the second end of the spring mounted on the axle.
26. The suspension mechanism of claim 20 , wherein the ratio between the rotational displacement of the first rotary drum and the effective rotational displacement of the spring ranges from about 1.5 to 1 to about 5 to 1.
27. The suspension mechanism of claim 23 , wherein the axle is fixed from rotation.
28. The suspension mechanism of claim 27 , wherein the transmission system comprises a winding gear connected to the first rotary drum and a loading gear connected to the second rotary drum, the winding gear and the loading gear configured to rotate at different rotational displacements to set a differential rotation rate between the first and second rotary drums.
29. The suspension mechanism of claim 28 , wherein the winding gear is connected to the loading gear by a pinion gear.
30. The suspension mechanism of claim 27 , wherein the ratio in the differential rotation rate between the first rotary drum and the second rotary drum is greater than about 1.5 to 1 and less than about 5 to 1.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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US11/392,340 US20070227677A1 (en) | 2006-03-29 | 2006-03-29 | Cordless window covering |
TW095128934A TW200736488A (en) | 2006-03-29 | 2006-08-07 | Cordless window covering |
CNA2006101150497A CN101046142A (en) | 2006-03-29 | 2006-08-17 | Cordless window covering |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/392,340 US20070227677A1 (en) | 2006-03-29 | 2006-03-29 | Cordless window covering |
Publications (1)
Publication Number | Publication Date |
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US20070227677A1 true US20070227677A1 (en) | 2007-10-04 |
Family
ID=38557119
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US11/392,340 Abandoned US20070227677A1 (en) | 2006-03-29 | 2006-03-29 | Cordless window covering |
Country Status (3)
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US (1) | US20070227677A1 (en) |
CN (1) | CN101046142A (en) |
TW (1) | TW200736488A (en) |
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- 2006-03-29 US US11/392,340 patent/US20070227677A1/en not_active Abandoned
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- 2006-08-17 CN CNA2006101150497A patent/CN101046142A/en active Pending
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US20060278348A1 (en) * | 2005-06-14 | 2006-12-14 | Tai-Long Huang | Pull Cord Device and Window Covering Including The Same |
US7406995B2 (en) * | 2005-06-14 | 2008-08-05 | Tai-Long Huang | Pull cord device and window covering including the same |
US20080000592A1 (en) * | 2006-06-29 | 2008-01-03 | Tai-Long Huang | Cord-winding device for a window blind |
US20080035280A1 (en) * | 2006-08-09 | 2008-02-14 | Ke-Min Lin | Adjusting structure of a curtain for adjusting the angle of curtain blade |
US7832453B2 (en) * | 2006-08-09 | 2010-11-16 | Ke-Min Lin | Adjusting structure of a curtain for adjusting the angle of curtain blade |
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US8662135B2 (en) * | 2012-05-18 | 2014-03-04 | Shih-Ming Lin | String-guiding structure for a curtain-reeling device |
US8863812B2 (en) * | 2013-02-04 | 2014-10-21 | Ke-Min Lin | Window blind assembly and cord guiding device thereof |
US20140217142A1 (en) * | 2013-02-07 | 2014-08-07 | Ke-Min Lin | Cord guiding device for a window blind |
US8925615B2 (en) * | 2013-02-07 | 2015-01-06 | Ke-Min Lin | Cord guiding device for a window blind |
US20150136336A1 (en) * | 2013-11-15 | 2015-05-21 | Taicang Kingfu Plastic Manufacture Co., Ltd. | Cord-winding device for venetian blind |
US9127500B2 (en) * | 2013-11-15 | 2015-09-08 | Taicang Kingfu Plastic Manufacture Co., Ltd. | Cord-winding device for venetian blind |
US20150275572A1 (en) * | 2014-03-28 | 2015-10-01 | Taicang Kingfu Plastic Manufacture Co., Ltd. | Window shade |
US9435154B2 (en) * | 2014-11-05 | 2016-09-06 | Chin-Fu Chen | Blind body positioning mechanism for non pull cord window blind and window blind using the same |
EP3032024A1 (en) * | 2014-12-01 | 2016-06-15 | Chen, Chin-Fu | Curtain body locating mechanism of a curtain with no cord |
US20160340975A1 (en) * | 2015-05-19 | 2016-11-24 | Taicang Kingfu Plastic Manufacture Co., Ltd. | Window blind device |
US9874057B2 (en) * | 2015-05-19 | 2018-01-23 | Taicang Kingfu Plastic Manufacture Co., Ltd. | Window blind device |
US20170211319A1 (en) * | 2016-01-22 | 2017-07-27 | Nien Made Enterprise Co., Ltd. | Window covering system and window covering control apparatus thereof |
US10428899B2 (en) * | 2016-01-22 | 2019-10-01 | Nien Made Enterprise Co., Ltd. | Window covering system and window covering control apparatus thereof |
US10273748B2 (en) * | 2016-03-03 | 2019-04-30 | Chin-Fu Chen | Blind body actuator for non-cord window blind assembly |
US20170292322A1 (en) * | 2016-04-06 | 2017-10-12 | Nien Made Enterprise Co., Ltd. | System and device for window covering |
US10501985B2 (en) * | 2016-04-06 | 2019-12-10 | Nien Made Enterprise Co., Ltd. | System and device for window covering |
US11476098B2 (en) | 2017-03-31 | 2022-10-18 | Dublin City University | System and method for remote sensing a plasma |
US11466515B2 (en) * | 2017-08-10 | 2022-10-11 | Lewis Hyman Inc. | Lifting push-pull positioning curtain |
US10641039B2 (en) * | 2017-08-28 | 2020-05-05 | Sheen World Technology Corporation | Cord separator for blind cord winding mechanism |
US11072975B2 (en) * | 2018-04-24 | 2021-07-27 | Jumbo Home Deco. Corporation (Cayman) | Side-inserted cord rolling device for non-pull cord window blind |
US11261655B2 (en) * | 2019-05-23 | 2022-03-01 | Teh Yor Co., Ltd. | Window shade and spring drive system thereof |
US20220120133A1 (en) * | 2019-07-12 | 2022-04-21 | Leafy Windoware Co., Ltd. | Curtain cord retracting and releasing device and transmission mechanism thereof |
US20230140382A1 (en) * | 2021-11-04 | 2023-05-04 | Nien Made Enterprise Co., Ltd. | Cord retractor and window covering having same |
US12098593B2 (en) * | 2021-11-04 | 2024-09-24 | Nien Made Enterprise Co., Ltd. | Cord retractor and window covering having same |
Also Published As
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CN101046142A (en) | 2007-10-03 |
TW200736488A (en) | 2007-10-01 |
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Legal Events
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